Automatic tube cutting machine



p 1950 o. H. GITTER 2,521,004

AUTOMATIC TUBE cuw'rmc MACHINE Filed Aug. 24, 1948 3 Sheets-Sheet 1 IN V EN TOR.

197 TUBA/1 8 35 Sheets-Sheet 2 O. H. GITTE R AUTOMATIC TUBE CUTTING MACHINE Illa t Sept. 5, 1950 Filed Aug. 24, 1948 OR. am,

INVENT AFTOENZVS'.

P 1950 o. H. GITTER 2,521,004

AUTOMATIC TUBE CUTTING MACHINE Filed Aug. 24, 1948 5 Sheets-Sheet 3 3; M2 I L INV 011 4 Aim 72? mmza Patented Sept. 5, 1950 AUTOMATIC TUBE CUTTING MACHINE Orville H. Gitter, Appleton, Wis assignor to Appleton Mfg. 00., Appleton, Wis., a corporation of Wisconsin Application August 24, 1948, Serial No. 45,908

(Cl. ice-c) 11 Claims.

This invention relates to improvements in machines for cutting paper tubing, and more particularly to machines of this type which operate automatically. More specifically this invention is an improvement on the machine disclosed in my prior application, Serial No. 703,183, filed October 19. 1946.

A general object of the invention is to provide a paper tube cutting machine adapted for large scale commercial operations, which produces smoothly and evenly severed tubes of a desired length with uniformity f operation.

A further object of the invention is to provide a machine of the class described wherein the various steps in the operation thereof are controlled by an electrical circuit.

A further object of the invention is to provide a machine of the class described wherein the operation of the mandrel jaws and of the cut-oil knife are each responsive to the movement of separate hydraulic rams.

A further object of the invention is to provide a machine of the class described having an automatic mechanism for intermittently feeding the uncut tube stock longitudinally along the mandrel.

A further object of the invention is to provide a machine of the class described having a target mechanism mounted adjacent the end of the mandrel thereof, said target mechanism being provided with an electric switch which is actuated by the contact of an uncut tube being fed along the mandrel.

A further object of the invention is to provide a machine of the class described wherein the portion of the target mechanism which is engageable by the paper tube, is swingable out of contact with said tube simultaneously with the severing operation, to permit ejection of the severed portion of the tube from the mandrel.

A further object of the invention is to provide a machine of the class described wherein the tube feeding mechanism is automatically stopped when the supply of uncut tube stock on the mandrel is exhausted.

A further object of the invention is to provide an automatic machine for cutting paper tubes wherein the mandrel shaft clutch mechanism and the tube feeding mechanism are interconnected in a manner to permit operation of the tube feeding mechanism only when the severing knife is out of engagement with the tube stock.

A further object of the invention is to provide a machine of the class described wherein the tube feeding mechanism is automatically reset by the introduction of a new piece of uncut tube stock onto the mandrel thereof.

A further object of the invention is to provide a machine of the class described wherein the reciprocable carrier for the severing knife is provided with a pair of switches which are actuated by movement of said slide, said switches, along with the target mechanism switch, functioning to control the automatic operations of the machine.

A further object of the invention is to provide a machine of the class described wherein the movement of the severing knife into operative position lags behind the movement of the mandrel shaft clutch into engaged positions by reason of a spring loaded sequence valve positioned in the supply line leading to the hydraulic ram which actuates said severing knife, said line originating at a source of fluid pressure which is common to both the severing knife ram and the hydraulic ram which actuates the mandrel shaft clutch.

A further object of the invention is to provide a machine of the class described having a continuously operating hydraulic pump which is connected to the conduits leading to the hydraulic rams thereof through a solenoid operated four-way valve, said solenoid being an integral part of the electrical circuit which controls the operation of the machine.

With these and other objects in view, the invention consists of the improved tube cutting machine and all of its parts and combinations as set forth in the claims, and all equivalents thereof.

In the drawings accompanying and forming a part of this specification wherein is shown one complete embodiment of the preferred form of the invention, and wherein the same reference numerals indicate the same parts in all of the views:

Fig. 1 is a side view of the improved tube cutting machine with an extent of tube stock in position on the mandrel thereof and in engagement with the target, parts being broken away and shown in longitudinal section;

Fig. 2 is a fragmentary plan view of the improved tube cutting machine, parts being broken away and shown in section;

Fig. 3 is a vertical sectional view taken along the 1ine.33 of Fig. 1;

Fig. 4 is a view taken along the line 4-5 of Fig. 1:

Fig. 5 is an enlarged detail sectional view of the sequence and needle valve taken along the line 5-5 of Fig. 2;

Fig. 6 is an enlarged detail vertical sectional view. of the four-way valve showing the plunger thereof in depressed position;

Fig. '7 is a sectional view similar to Fig. 6 only showing the valve plunger in normal position;

Fig. 8 is an enlarged vertical sectioifal view taken along the line 8-8 of Fig. 2;

Fig. 9 is an enlarged fragmentary view partly in section showing the construction of the rotatable expanding jaw assembly at the outer' end of the mandrel with the Jaw segments in retracted position; I V

Fig. 10 is a view similar to Fig. 9 only showing the relationship of the component parts when the jaw segments are expanded into engagement with the tube stock; and

Fig. 11 is a schematic diagram of the electrical circuit which controls the operation of the improved tube cutter.

Referring more particularly to the drawing it will appear that a supporting table or elevated frame for the improved tube cuttingmachine is indicated generally by the numeral 5. The table .|5 has a top l6 formed of longitudinal side members I1 and 8 and preferably has transverse plate members I9 and 20, ,as well as transverse end members 2| and 22. At the outer end of the top I6 there is a fixed transverse bed 23. Mounted on the top surface of the bed 23, through tongue and groove connections 24, is a cross slide member '25 which is transversely 'reciprocable relative to the table top l6. Mounted on top of the slide 25, at the far end thereof relative to Figs. 1 and 2 and movable therewith, is an upright standard 26 which is adapted to replaceably hold, in substantially horizontal position, a severing knife or cutter 2'I The top l6 of the table I5 is provided near its outer end with a rearwardly projecting shelf 28. Mounted on the shelf 28 and operative on a horizontal transverse axis is a double acting hydraulic' ram 29. The piston rod 30 of the ram 29 is fixedly connected to the rear end of the slide;

' member 25 as shown in Fig. 2. The ram 29 is member 25 and is engageable with the plunger 35 of the switch 33 as shown in Fig. 2.

A normally closed electrical push button switch 8 36; having a plunger 3'1, is fixedly mounted on the top face of the bed 23 adjacent the outer edge of the slide member 25 and preferably at the opposite end thereof from the switch 33. .An angle bracket 38 is fixedly mounted on the outer edge of the slide 25 and is engageable with the plunger 31 of theswitch 36. Forward movement of the cross-slide 25 from the position of Fig. 2 will cause bracket 34 to depress the plunger 35 of the switch 33 thereby closing the contacts of said switch.

Further forward movement of the cross-slide will cause the bracket 38 to depress the plunger 31 of the switch 36 to open the contacts thereof.

Rearward movement of the slide 25 will permit the plungers of the switches 33 and 36 to return to their normal undepressed positions, thereby restoring the contacts a of said switches to normal position.

Mounted on the inner end of the table top l6 are a pair of spaced inverted U-shaped brackets 39 which rigidly support a horizontal tubular mandrel 40.

A mandrel shaft 4| is mounted on suitable bearings and extends axially of the mandrel 4|]. The shaft 4| projects beyond the inner end of the mandrel 48 as well as slightly beyond the outer end thereof. 0n roller bearings carried by the shaft 4| adjacent the inner end of the mandrel 40 is an annular collar 42. Pivotally mounted at its lower end on'the plate I 9 is a yoke 43 (see Fig. 3) having an annular ring portion 44, a short arm 45 projecting vertically upwardly therefrom and a supporting arm 46 projecting downwardly in a diametrically opposite direction from the arm 45. The collar 42 is pivotally connected to the yoke 43 by a pair of bolts 41 which extend horizontally in the same diametrical line.

A U-shaped bracket 48 embraces the exterior of the mandrel 4| between the brackets 33. Fixedly mounted on. the top of the left hand bracket 33, as viewed in Figs. 1 and '2, and on the top of the bracket 48 is a double-acting hydraulic ram 49. The ram 49 is mounted with its piston rod 50 projecting parallel with the axis of the mandrel 4| and to the left, as viewed in Figs. 1 and 2. The end of the piston rod 50 is pivotally connected to the upper end of the arm 45 of the yoke 43, as by the forked connection member 5 and the pin 52.

- The hydraulic ram 43 is provided with an aperture 53 near the inner end of the casing thereof and is further provided with an aperture 54 near the outer end of said casing. Axial movement of the piston rod of the ram 49 causes pivotal movement of the yoke 43 about the lower end of its arm 46, and this movement causes sliding axial movement of the collar 42 along the shaft 4|. As the collar 42 is reciprocated toward the left relative to Figs. 1 and 2, it will abut an an idler pulley 55 which is revolu'bly mounted on the shaft 4 I.

There is affixed to the inner face of the idler pulley 55 a clutch plate 56, and the initial axial movement of the idler pulley 55 to the left relative to Figs. 1 and 2 causes the clutch plate 56 to compress a coiled spring 51 surrounding an inner end portion of the shaft 4| and bearing against a cap 58 which is fast to the outer end of the shaft 4 I. This reciprocates the shaft 4| to the left, relative to Figs. 1 and 2, for a purpose later to be described. Further movement of the pulley 55 toward the left on the shaft 4| causes the clutch plate 56 to frictionally engage the adjacent face of a clutch disc 59 which is scrrewed fast on the shaft 4|, causing said shaft to revolve by virtue of endless driving belts 60 which engage the idler pulley 55, and which also engage a pulley 6| on the shaft of a continuously operating electric m0- tor 62.

At the outer end of the shaft 4| there is operatively mounted an expanding jaw assembly (see Figs. 9 and 10) which is retained against outward axial displacement by a snap ring 62 positioned in a circumferential groove 63 in the shaft 4|. Mounted on the shaft 4| is an annular wedge, member 64 whose sleeve portion at its inner end, has an outer tapered surface 55 to wedgingly engage similarly taperedinner surfaces on the hub portions 66 of jaw segments 61. Keyed to the shaft 4| is the hub of a bushing 68 having an outwardly offset annular portion which extends into the recesses 61' therefor in the jaw segments 61. The jaw segments 61 are radially movably mounted on the offset portion of the bushing 58 by filister head screws 69 fixed to said bushin and having the heads thereof located in enlarged recesses Til therefor in the jaw segments 57.

From the description thus far given of the expanding jaw assembly, it should be obvious that a reciprocation of the shaft M to the left relative to Figs. 1 and 2, through the means previously described, is effective to cause movement of the wedge member 64 from its outer normal position of Fig. 9 to its inner jaw expanding position of Fig. 10. In so moving, the wedge member 6 3 compresses a coiled spring 518 confined in a space between the flanged head of the wedge member 54 and the internal annular flange of a casing member H, which is in splined association with the wedge member 64. The jaw segments 61 are ieldingly held in their normal retracted positions by encircling band springs 12. When the wedge member it is moved inwardly to the position of Fig. 10, it forces the jaw segments 67 radially outwardly so that their outer knurled surfaces project beyond the outer periphery of the mandrel 4G to clampingly engage the inner surface of the elongated cylindrical tube stock 13, which had previously been introduced onto the manrel M.

The numeral 1 3 indicates a target assembly which is carried by an arm mounted fast on the outer end of a shaft l6 journaled for rotation and for longitudinal adjustment in the frame of the table It. Referring to Figs. 1, 2, 4 and 8, the target assembly It consists of a substantially rectangular plate-like fram member ll, which extends substantially in a vertical plane. The member H is formed with a pair of spaced unthreaded longitudinally extending apertures '88 and with a central longitudinally extending aperture it, which is formed with screw threads. A

pair of spaced rods til project from the inner face of the arm "l5 and slidably fit into the apertures E8 of the frame 'IE, thereby providing a support for said frame which permits longitudinal sliding movement thereof. The arm 75 is formed with an aperture M which is alined with the aperture E9 in the frame H. An adjustment screw 82 is threadedly positioned in the aperture IQ of the frame Ti and has an unthreaded portion of reduced diameter which projects through the aperture st of the arm 15. To the outer end of the screw 82 is fixed a knob 83. The construction of the turning screw B2 is such that it cannot move longitudinally. Rotative movement of the screw 82 causes longitudinal movement of the frame member ll.

Referring more particularly to Figs. 1, 2 and 4. the target member Ed is connected to' the lower edge of the frame member T! in a manner to permit both pivotal and limited longitudinal movement of said target member. A fixed pin 85 (see Fig. 1), having an enlarged head, is an integral part of the pivotal mounting above mentioned, and its head portion limits the outward longitudinal movement of the target R3 3. The target 86 is formed with a flat plate portion 8b which extends rearwardly from the frame H in a horizontal plane and is also formed with portion 81, which projects at right angles from the portion 86 and is spaced from the forward face of the frame member TI. The portion 81, at its upper end, is curved awa from the frame member 71 as shown in Fig. 4, and in addition, it extends inwardly (to the left) beyond the frame member I1 as shown in Figs. 1 and 2. The target member Bl is provided at its inner end with a substantially crescent-shaped plate member 88, which is adapted to be engaged by the outer end of the tube stock it, as shown in Fig. 1, to form a stop and a gauge therefor when in the position shown in Figs. 1, 2 and 4.

A substantially rectangular plate member 39 projects rearwardly and at right angles from the outer end of the frame member H. A normally open electrical push button switch 98 is mounted on the inner face of the frame member 89 near the rear edge thereof. The plunger 9i of the switch Si? is preferably enclosed by a sleeve $2 in the manner shown in Fig. 8. An internally threaded sleeve 931s fixedly mounted on the frame member near the rear edge thereof and in line with the sleeve 92 of the switch 9i] (see Fi 2). An adjustment screw 9% having a knurled head 95 is mounted in the sleeve 93 as shown in Fig. 8. A link 9b is positioned with one end'in the sleeve 93 and in engagement with the end of the screw 9t and with its other end in the sleeve 92 of the switch 95. In Fig. 8 it will be noted that the end of the link 56 in the sleeve 92 is not in contact with the plunger st of the switch 90. This relationship exists when the portion 86 of the target it is pivoted downwardly and does not correspond to the normal position for these parts shown in Fig. 4. In Fig. i, the portion 86 of the target 86 is pivoted upwardly to its normal horizontal position. In its normal position, the link 96 more closely approaches a horizontal position, and its end within the sleeve 92 is positioned substantially in contact with the plunger ti without depressing said plunger. With the link 96 in its normal position, longitudinal outward movement of the target 8% will cause the link as to depress the plunger 9! of the switch at, thereby closing the contacts thereof.

Referring to Figs. 2- and 4, a coiled spring 97 is connected at one end of a lug 98 which projects rearwardly of the frame member ll adjacent the inner end thereof. The opposite end of the spring ii? is connected to the portion, 86 of the target at near its inner edge. It will be noted that the coiled spring 37 exerts an inward pull on the target 86 (to the left in Figs. 1, 2 and 8), as well as an upward pull on the portion 86 thereof. A solenoid 99 having-a plunger Hill is mounted on the rear face of the frame member 5?, with the plunger Hill extending along a vertical axis. When the solenoid 99 is energized, the plunger it!) thereof is forced downwardly against the portion 86 of the target 8 3, thereby causing counter clockwise pivotal movement of the target 85, as viewed in Fig. 4, against the tension of the spring 91. When the solenoid 99 is not energized, the spring 91 holds the portion 86 of the target at in its normal horizontal position.

Referring to Fig. 1, the numeral we indicates a continuously operating hydraulic pump and tank unit which is driven by the motor 62 through a coupling M2. The pump in the unit B0! is preferably provided with a suitable pressure relief valve in its discharge line. Mounted on top of the unit it! is a four-way spring loaded twoposition valve M3. The valve N33 has a plunger IM which is actuated through a pivotal lever Hi5 by the plunger We of a solenoid l0? mounted. on top of the valve )3. Energization of the solenoid Hl'l causes'ejection of the plunger I06 therefrom (to the left in Fig. 1), causing counterclockwise pivotal movement of the lever Hi5, and

movement of the plunger I04 to the right as viewed in Figs. 1, 6 and '1.

Referring to Figs. 6 and 7, the valve I03 is formed with a bore I08 in which the plunger I04 I is slidably mounted, there being a coil compression spring I09 positioned between the inner end of the plunger ,I04 and the inner end of the bore I08. Three preferably equally spaced passages I I 0, III and I I2 communicate with the bore I08 along the upper surface thereof, and three similarly spaced passages I I3, I I4 and I I5 communi cate with the bore I08 at points diametrically opposite from those of the passages I I0, III and H2 respectively, as shown in Figs. 6 and '7.

The plunger I04 is formed with a recess I15 at its outer end to receive the lower end of the pivotal lever I05. At a pointspaced from the inner end of the plunger I04, 'said plunger'is formed with a pair of recesses I16 and I11, which extend inwardly from diametrically opposite side portions thereof, as is shown in Figs. 6.and 7. The recess I16 15 01 a length to permit communication by said recess with either the passages IIO and I II or the passages I II or II2, depending upon the position of the plunger' I04. The recess I11 is of the same length, and can communicate with the passages m and m, or H4 and n5,

depending upon the position of the plunger 104 as shown in Figs. 6 and '7.

The passages H and II are interconnected as shown, and communicate with a conduit I I6 which leads to the tank or reservoir of the unit II. The passages 'II3 and II2 are interconnected, as shown, and communicate with a conduit III, which leads to .the discharge side of the pump in the unit IOI. The passage III com-1 municates with a conduit I I8, which in turn communicates with the aperture 54 of the hydraulic ram 49 and with the inlet to a combination sequence and speed control valve II9. From the outlet of the sequence and speed control valve II 9, a conduit I20 leads to the aperture III of the hydraulic ram 29. The passage II4 of the valve I 03 communicates with a conduit I2I, which in turn communicates with the aperture 53 of the hydraulic ram 43, as well as the aperture 32 of the hydraulic ram 29.

The normal position of the plunger I04 of the valve I03 is that shown in Fig. 7. In this position hydraulic fluid under pressure enters the conduit II1, passes up through the passages H3, through the recess I11, through the passage II 4 and out through the conduit I2I to the hydraulic ram 49 and 29. Hydraulic fluid returning from the rams 49 and 29 enters the valve I03 through the conduit I I8, passes through the passage III,

passage I28 having a bevelled annular seat I24 at one end. Positioned in the bore I22 is a plunger I 25 having a frusto-conical lower end which co-operates with the seat I 24. The plunger.I26 is urged against the seat I24 by a compression spring I26 which is adjustably held within the bore by an adjustment screw I21. One end of a passage I28 communicates with the bore I22 at a point above the seat I24 and the other end thereof communicates with the bottom of a chamber I29. An adjustment screw I30 is threadedly mounted in the body of the valve H9 and has a conical lower end which is positioned in the chamber I29 and which may be adjusted to restrict the opening of the passage I 28 into the bottom of said chamber. The adjustment screw is preferably formed with a knurled head I3I. A passage I32 communicates with the side meal] of the chamber I29 and with the conduit A normally open, triple-pole, single throw solenoid actuated relay I33 is preferably mounted on the sidemember I8 of the table I5. Referring more particularly to Fig. 11 wherein is shown a schematic wiring diagram of the electrical circuit which controls the operation of the improved tube cutting machine, itwill be noted that the relay I33 has a holding coil I34 and three sets through the recess I16, through the passage II 0,

and back to the reservoir, through the conduit IIB. When the solenoid I 01 is energized, the plunger I04 of the valve I03 is moved to the position of Fig. 6, and in so doing compresses the spring I09. When the plunger I04 is in this position, hydraulic fluid under pressure enters through the conduit II1, passes through the passage II2, through the recess I16, through the passage III, and out via the conduit II8 to the hydraulic rams 49 and 29. Hydraulic fluid returning from the hydraulic rams 49 and 29 enters the valve I03 through the conduit I2I, passes through the passage II 4, through the recess I11, through the passage I I5 and baclr to the reservoir through the conduit I I6.

, Referring to Fig. 5, the combination sequence and speed control valve 9 has a bore I 22, which communicates with the conduit II8 through a of normally open electrical contacts I35, I36 and I 31. Leading from one side of a suitable source of electrical current I38, a line I39 connects with one side of the normally open switch I 33, one side of the contacts I35 andone side of the solenoid I34. .A line I 40 connects from the other side of the source I38 to one side of the contact I36, one side of the solenoid 99 and one side of the normally closed switch 36. A line I connects the other side of the switch 33 with the other side of the solenoid 99. A line I42 connects the other side of the switch 35 with one side of contacts I31. A line I43 connects the other side of the holding coil I34 with the other side of the contacts I31, and the solenoid I01 is connected across the other side of the contacts I36 and I36. The normally'open switch 90 is connected across the contacts I31.

Referring to Figs. 1 and 2, the numeral I44 indicates a source of continuous variable speed rotatable power such as an electric motor having a. pulley I45. A transverse shaft I46 is rotatably journalled, as in bearings I41 and I48, mounted on the members I1 andv I8 of the table I5 respectively. A pulley I49 is rigidly mounted on the shaft I46 substantially midway between the bearings I41 and I48. The numeral I50 indicates an idler pulley which is freely rotatable on the shaft I46 and around which extends a driving V-belt I5I which also extends around the pulley I45. The construction of the pulley I50 is such that it engages one side face and the inner face of the V-belt I5I. Mounted on the shaft I46 for limited rotatable movement outwardly of'the pulley I50 is a disc I52.- A hub I53 is rigidly mounted on the shaft I46 outwardly of the disc I52 and the disc I52 is connected to the hub I53 through a torsion spring I54, which is connected at one end to said hub and at the other end to said disc. The deformation of the torsionspring I54 limits the rotation of the disc face I52, which is adapted to engage the side of the belt I5I opposite the pulley I50. A suitable compression spring I is positioned on the 8 shaft I46 between the pulley I50 and the disc I52, and urges said pulley and said disc in opposite directions.

Freely rotatable on the shaft I46 and positioned between the bearing I48 and the pulley I50 is a pair of cam sleeves I55 and I55. The sleeves I55 and I56 have co-operating cam surfaces which, when the sleeves .are rotated in opposite directions, cause said sleeves to move apart, thereby forcing the pulley I50 outwardly against the disc I52 while at the same time compressing the spring I80 therebetween. The cam sleeve I56 is provided with an upstanding lug I51, and a link I58 is pivotedly connected at one end to the lug I51 and at the other end to one of the-bolts 41 on the yoke 43 The cam sleeve I55 is formed with-.a downwardly projecting lug I58. A pulley I60 is revolubly mounted on an arm I6I, which in turn is mounted on the plate 20, and an endless cable I62 extends around the pulleys I48 and I60, both the upper and lower extents of the cable I62 being substantially parallel with the axis of the mandrel 40. A transverse shaft I63 is rotatably mounted on suitable bearings, such as I64 and I65. Fixed on the inner end of the shaft I63 adjacent the cable I62 is an upstanding arm I66 having an eye portion I61 through which the lower extent of the cable I62 extends. Rigidly mounted on the shaft I63, preferably outwardly of the bearing I64, is an off-center lever I68. The lever I68 is in the form of a bell crank having an arm I68, which is normally in contact with a suitable stop I10. A cable I1I is connected at one end to the lug I58 of the cam sleeve I55 and is connected at the other end to the arm I69 of the off-center lever I68. Fixidly connected to the upper extent of the cable I62 is a yoke I12 which may have an annular shape and which slidably embraces the mandrel 40. Fixedly connected to the cable I62 is a collar I13. The pulley I60 is formed with a suitable notch I14 to permit the collar I13 to pass therearound with the cable I62.

Operation is moved to the left to cause a slackening of the cable I1I. The target 84 is pivoted upwardly sllfilciently to permit the introduction of an elongated extent of tube stock 13 onto the mandrel 40 from the outer end thereof. As the tube stock 13 is so introduced, it abuts the yoke I 12 which embraces the mandrel 40 and moves said yoke inwardly (to the left in Figs. 1 and 2). Inward'movement of the yoke I12 causes simultaneous movement of the upper extent of the cable I62 in the same direction. The target is then allowed to return to its normal position and the targetassembly is then adjusted by turning the knob 83 in a direction to space the plate 88 of the target 84 outwardly of the severing knife 21 a distance substantially equal to the length of the sections into which the tube stock 13 is to be cut. Very fine adjustments may be made in the position of the target assembly by turning the knob 83. Where. it is desired to materially change the length of tube sections to be cut, the target assembly may be shifted by moving the shaft 16 inwardly or outwardly the desired amount.

To start the automatic operation of the machine, the oif-center lever I68 is moved to the right to the, position shown in Figs. 1 and 2. This causes a tightening up of the cable "I and rotates the cam sleeve I55 in a counterclockwise direction as viewed in Fig. 1, while at the same time the cam sleeve I56 is held stationary by the link I58. This relative movement of the cam sleeves results in outward movement of the cam I55 along the shaft I46, pushing the pulley I50 outwardly therewith along said shaft. As the pulley I50 moves outwardly, the constantly moving belt I5I engages the disc I52 along its surface I52, causing said disc and the shaft I46 to rotate ina clockwise direction as shown in Fig. 1. As the shaft I46 rotates, the pulley I48 also rotates and causes the upper extent of the cable I62 and the yoke I12 to move outwardly (toward the right as viewed in Figs. 1 and 2). As the yoke I12 so moves, it pushes the tube stock 13 in abutment therewith to the right until the outer end of the tube stock 13 engages the plate 88 of the target 84. Engagement of the tube stock 13 with a plate 88 moves the target 84 outwardly into engagement with the head of the fixed hinge pin 85. When the target is thus moved, the link 86 (see Fig. 8) depresses the plunger 8I of the switch 80, thereby closing the contacts of said switch.

Referring to Fig. 11, closing the contacts of the switch causes energization of the holding coil I34 of the relay I33, thereby closing the contacts I35, I36 and I31. Closing of the contacts I35 and I36 causes energization of the solenoid I01 which moves the plunger of the valve I03 to the position shown in Fig. 6. This position of the valve I03 causes hydraulic fluid under pressure to pass out of the passage III of the valve I03, through the conduit II8 to the aperture 54 of the hydraulic ram 48 and to the sequence and speed control valve H8. The piston of the ram 48 is immediately moved toward the left as viewed in Figs. 1 and 2, thereby pivoting the yoke 43 to the left to engage the idler pulley 55 and move it to the left. This causes the shaft 4| to be moved to the left and then to be rotated, expanding the jaws 61 prior to said rotation, in the manner previously described to engage the tube stock.

Rotation of the expanded jaws 61 causes rotation of the tube stock 13 therewith about the mandrel 40.

As the yoke 43 moves toward the left into clutch engaging position, the link I58 is pulled to the left therewith to permit the sleeve cam I56 to rotate in a counterclockwise direction to allow the sleeve cam I 55 to move inwardly along the shaft" I46 into the relationship shown in Fig. 2.

This permits the pulley I50 to move inwardly along the shaft I46 and disengages the belt I5I from the disc I52, stopping rotation of the shaftv I46 and the pulley I49. Stopping of the pulley I48 stops the movement of the cable I62 and the yoke I12 to thereby stop the movement of the stock 13 along the mandrel 40. Any rotation of the disc I52 which takes place between the instant the target 84 is engaged by the tube stock 83 and the movement of the yoke 43 to the left is absorbed by the torsion spring I54 which connects the disc I52 to the hub I53 which is fixed on the shaft I 46.

Hydraulic fluid entering the sequence and speed control valve II8 must lift the plunger I25 off the seat I24 against the pressure of the spring I26 before said fluid can fiow into the passage I28, past the speed control needle I30 and out the conduit I20. The hydraulic fluid under pressure flows through the conduit I20 to the aperture 3I of the hydraulic ram 28, but because of the spring 11 loaded plunger I28 in the valve II8, there is a momentary lag between the operation of the hydraulic ram 48 and that of the ram 28. This lag results in the tube stock 13 being rotated prior to forward movement of the severin knife 21 into engagement therewith by the ram 28.

As the cross slide 28 is moved forward by the hydraulic ram 28, the angle bracket 34 on the side of said slide depresses the plunger 38 of the switch 33, thereby closing the contacts thereof. Referring again to Fig. 11, energization of the solenoid 88 of the target assembly 14 is effected, and the plunger I88 pivots the target 84 about the hinge pin 88, in a, counterclockwise direction as viewed in Fig. 4, against the tension of the spring 81. This pivotal movement is relatively short, but it is suflicient to move the plate 88 of the target 84 upwardly out of contact with the outer end of the tube stock 13 to permit the severed section thereof to pass past the plate 88 of the target 84.

As the cross slide 28 continues to move for- I ward, it effects cut-oil of a section of tubing,

and in'addition, the bracket 38 depresses the plunger 31 of the switch 38 to open the contacts thereof. This de-energizes the holding coil I34 (see Fig. 11) and opens the contacts I35, I38 and I31, thereby de-energizing the solenoid I81 and allowing the spring I88 in the valve I83 to move the plunger I84 thereof to its normal position "shown in Fig. '1. when the valve I83 is in the position of Fig. '1, hydraulic fluid passes through the conduit I2I to the aperture 83 of the ram 48,;and to the aperture 32 of the ram 28. This :causes movement of the yoke 43 to the right and also causes rearward movement of the cross slide 28. Return of the cross slide 28 to its normal position opens the contacts of the switch 83 thereby deenergizing the solenoid 88 of the target assembly 14. Deenergization of the solenoid 88 permitsthe spring 81 to pull the target 84 both longitudinally inwardly (to the left in Fig. 2) and in a clockwise direction (as viewed in Fig. 4) to thereby return it to its normal position wherein the plate 88 thereof will again be in the path of the tube stock 13 as it is fed outwardly along the mandrel during the next cycle of operation.

Return of the cross slide 25 also closes the con-- tacts of switch 36.

As the yoke 43 moves to the right the expanding jaws 81 disengage the tube stock 13 and then the shaft 4| stops rotating. Movement of the yoke 43 to the right also causes movement of the link I88 to the right, thereby causing the cam I58 to rotate in a clockwise direction as viewed in Figs. 1 and 2. Since the cam I58 is held against clockwise movement beyond the limits permitted by the cable "I connected thereto, movement of the yoke 43 to the right causes a rotational movement of the cam I58 relative to the cam I88 which results in movement of the cam I58 outwardly along the shaft I48. As the cam I55 again so moves, it pushes the pulley I58 outwardly and engages the constantly moving belt III with the disc I52, causing it and the shaft I48 to rotate. As previously described, rotation of the shaft I 48 causes the yoke I12 to push the tube stock outwardly along the mandrel toward the target 84, thereby starting a new cycle.

As the tube stock 13 is cut into a plurality of sections of predetermined length by a series of the cut-off cycles like the one hereinbefore described, the yoke I12 approaches the outer end of the mandrel 48, and the collar I13 which is fixed on the cable I82, approaches the eye I81 of invention and all of such changes are contemthe arm I88 on the transverse shaft I83. At a predetermined point in this movement of the cable I62 the collar I13 engages the eye I81 and moves it to the left as viewed in Figs. 1 and 2. This rotates the shaft I83 in a counterclockwise direction as viewed in Fig. 1 and swings the offcenter lever I88 to the left, thereby releasing the tension on the cable I1I. As long as the cable "I is slack, there can be no relative movement of the cams I55 and I58, and consequently there will be no outward movement of the yoke I12. While the coaction of the collar I13 and the eye I81 stops all feeding action by the yoke I12 at the outer limit of its travel, it is apparent that the feeding of the tube stock 13 along the mandrel 48 may be stopped by the operator at any time by manually moving the lever I88 to the left and thereby slackening the cable I".

The degree to which the operation of the hydraulic ram 28 lags behind that of the ram 49 during a cut-off cycle'may be varied by adjusting the screw I21 of the valve II8 to vary spring load on the plunger I25 thereof. The speed with which the ram 28 moves can also be easily adjusted by means of the speed controlling screw I3I of the valve II8, which controls the rate of flow of hydraulic fluid to the ram 28 through the conduit I28.

Various changes and modifications may be made without departing from the spirit of the plated as may come within the scope of the claims.

What is claimed as the invention is:

1. In a tube cutting machine, a tubular stock supporting mandrel, a shaft. extending axially through said mandrel, said shaft being reciprocable and rotatable relative to the mandrel, means on said shaft responsive to reciprocatory movement of the shaft for clamping the stock, a source of rotative power, means including a hydraulic ram for causing reciprocatorymovement of said shaft and for causing rotation of said shaft by said source of rotative power, and a cut ter movable into and out of stock rotated on said mandrel.

2. In a tube cutting machine, a tubular stock supporting mandrel, a shaft extending axially through said mandrel, said shaft being reciprocable and rotatable relative to-the mandrel, means on said shaft responsive to reciprocatory movement of the shaft for clamping the stock, a source of rotative power, meam including a hydraulic ram for causing reciprocatory movement of said shaft and for causing rotation of said shaft by said source of rotative power, a cutter movable into and out of stock rotated on said mandrel, a second hydraulic ram for operating said outter, and fluid pressure and return conduits connected to said hydraulic rams.

3. In a tube cutting machine, a tubular stock supporting mandrel, a shaft extending axially through said mandrel, said shaft being reciprocable and rotatable relative to the mandrel, means on said shaft responsive to reciprocatory movement of the shaft for clamping the stock, a source of rotative power, a clutch mounted on said shaft and having a rotating member driven by said source of power, an hydraulic ram for actuating said clutch to cause reciprocatory movement of said shaft and to cause rotation of said shaft with said rotating clutch member, and a cutter movable into and out of stock rotated on supporting mandrel, a shaft extending axially through said mandrel, said shaft being reciprocable and rotatable relative to the mandrel, means on said shaft responsive to reciprocatory movement of the shaft for clamping the stock, a source of rotative power, a clutch mounted on said shaft and having a rotating member driven by said source of power, an hydraulic ram for actuating said clutch to cause reciprocatory movement of said shaft and to cause rotation of said shaft with said rotating clutch member, a cutter movable into and out of stock rotated on said mandrel, a second hydraulic ram for operating said cutter, and fluid pressure and return conduits connected to said hydraulic rams.

5. In a tube cutting machine, a tubular stock supporting mandrel, a shaft extending axially through said mandrel, said shaft being reciprocable and rotatable relative to the mandrel, stock clamping jaws carried by the shaft and actuated by reciprocation thereof, a clutch mounted on said shaft and having a freely rotatable member, means for rotating said rotatable clutch member, means for engaging said clutch to cause rotation of said shaft, operation of said clutch engaging means being also effective to reciprocate said shaft, means for mechanically moving stock along said mandrel, and interlocking means for rendering said stock moving means inoperative when said clutch is engaged. I

6. In a tube cutting machine, a tubular stock supporting mandrel, a shaft extending axially through said mandrel, said shaft being reciprocable and rotatable relative to the mandrel, stock clamping jaws carried by the shaft and actuated by reciprocation thereof, a clutch mounted on said shaft and having a freely rotatable member, means for rotating said rotatable clutch member, means for engaging said clutch to cause rotation of said shaft, operation of said clutch engaging means being also operative to reciprocate said shaft, a pusher member adjacent the mandrel for moving stock therealong, and interlocking means for stopping said pusher member at a predetermined point.

7. In a tube cutting machine, a tubular stock supporting mandrel, a shaft extending axially through said mandrel, the shaft being recipro cable and rotatable relative to the mandrel, a clutch mounted on said shaft and having a freely rotatable member, means for rotating said freely rotatable member, stock clamping jaws carried by the shaft, means for actuating said jaws and said clutch, a cutter movable into and out of stock rotated with said clamping jaws, a stock moving member mounted adjacent said mandrel for movement longitudinally thereof, drive means extending to said member, a second clutch for controlling said member drive means, and means interlocking both of said clutches to normally engage said second clutch upon disengagement of said first clutch.

8. In a tube cutting machine, a tubular stock supporting mandrel, a shaft extending axially through said mandrel, the shaft being reciprocable and rotatable relative to the mandrel, a clutch mounted on said shaft and having a freely rotatable member, means for rotating said freely rotatable member, stock clamping jaws carried by the shaft, means for actuating said jaws and said clutch, a cutter movable into and out of stock rotated with said clamping jaws, a stock moving member mounted adjacent said mandrel for movement longitudinally thereof, drive means extending to said member, a second clutch 14 for controlling said member drive means, means interlocking both of said clutches to normally engage said second clutch upon disengagement of said first clutch, and means connected to said second clutch for selectively preventing engagement thereof.

9. In a tube cutting machine, a tubular stock supporting mandrel, a shaft extending axially through said mandrel, the shaft being reciprocable and rotatable relative to the mandrel, a clutch mounted on said shaft and having a freely rotatable member, means for rotating said freely rotatable member, stock clamping jaws carried by the shaft, means for actuating said jaws and said clutch, a cutter movable into and out of stock rotated with said clamping jaws, a stock moving member mounted adjacent said mandrel for movement longitudinally thereof, drive means extending to said member, a second clutch for controlling said member drive means, means interlocking both of said clutches to normally engage said second clutch upon disengagement of said first clutch, a lever connected to said second clutch for selectively preventing engagement thereof, and means for actuating said lever upon movement of said stock moving member to a predetermined point in its travel to thereby render said second clutch unengageable.

10. In a tube cutting machine, a mandrel for supporting an elongated extent of tubing stock from which individual tubes of predetermined length are to be cut, a target assembly spacedly and adjustably mounted adjacent the outer end of the mandrel, means for moving the stock along the mandrel toward said target assembly, said target assembly carrying a pivotal target which is normally positioned in the path of the stock as said stock is moved along the mandrel, said target assembly also having a solenoid for pivotally moving said target out of the path of the stock, a cross slide movable laterally of the mandrel and carrying a cutter, means for moving the cross slide back and forth to move the cutter into and out of the rotating stock, an electrical switch actuated by inward movement of said cross slide, and an electrical circuit including said cross slide switch for controlling the operation of said stock moving means, said stock rotating means and said cross slide moving means, said circuit functioning upon actuation of said cross slide switch to energize said solenoid to thereby swing the target out of the path of the tube stock on the mandrel.

11. In a tube cutting machine, a mandrel for supporting an elongated extent of tubing stock from which individual tubes of a predetermined length are to be out, a target assembly spacedly and adjustably mounted adjacent the outer end of the mandrel, means for moving the stock along the mandrel toward said target assembly, said target assembly carrying a pivotal and longitudinally. movable target which is normally positioned in the path of the stock as said stock is moved along the mandrel, said target assembly having an electrical switch which is actuated by longitudinal movement of said target, and said target assembly also having a solenoid for pivoting said target out of the path of the stock, means for rotating the stock, a cross slide movable laterally of the mandrel and carrying a cutter, means for moving the cross slide back and forth to move the cutter into and out of the rotating stock, an electrical switch actuated by inward movement of the cross slide, and an elec trical circuit including said target assembly switch and said cross slide switch for controlling the operation of said stock moving means, said stock rotating means and said cross slide movin means, said electrical circuit functioning upon actuation of the target assembly switch to stop the stock moving means, and said circuit also functioning upon' actuation of the cross slide switch to energize said solenoid to thereby swing the target out of the path of the tube stock.

- ORVILLE H. GII'IER' REFERENCES ci'rnn (:be following references are of record in the fll of this patent:

Number Number 16 UNITED STATES PATENTS Name Date McGrath Mar. 19, 1912 Lawson Nov. 25, 1930 Libby Sept. 4, 1934 FOREIGN PATENTS Country Date Great Britain Aug. 20,1936 

